Control mechanism



June 16, 1959 w. H. D. BRoUsE CONTROL MECHANISM 3 Sheets-Sheet 1 I Filed Jan. 15. 1954 ZW-WIM Z /4 wl.

INVENTOR. Bzymmwe l a www June 16, 1959 w. H. D. BRousE CONTROL MECHANISM Filed Jan. 15. 1954 3 Sheets-Sheet 2 INVENToR w. H. DBRUSE coNTRoL MEcHANrsM June 16, 1959 5 Sheets-Sheet 3 Filed Jan. 15, 1954 coNoL MnCHANIsM William H. D. Brause, Toronto, Ontario, Canada, as-

signor to Teletlex Incorporated, Philadelphia, Pa., a corporation of Delaware Application .l'anuary 15, 1954, Serial No. 404,317

Claims. (Cl. 74-394) The present invention relates to a novel control mechanism and, more particularly, to a novel control mechanism for operating various devices in opposite directions, which devices often require the application of a relatively large force for initially starting them in either direction.

As is well known, many devices such as certain valves, windows and the like, often tend to stick in the 'position to which they have been adjusted so as to require the application of a relatively great starting force to subsequently move them to either an open or a closed position. However, once such device has been started, further movement may usually be accomplished with the application of a relatively small force and at the same time at relatively higher speeds.

It is an object of the present invention to provide a novel control mechanism for operating devices such as valves, windows and the like, by which mechanism a relatively large force may be applied for a predetermined interval to start the device at a relatively slow rate, whereupon the mechanism is automatically operable to increase the rate at which the device is operated.

Another object of the present invention is to provide a novel control mechanism for operating the devices such as valves, windows and the like, in opposite directions, which ldevice is capable of providing a relatively great force for starting the device in either direction and then increasing the rate of operation of the device.

Still another object of the present invention is to provide a novel control mechanism of the type described in the preceding paragraphs which is adapted to operate a device from a remote position.

A further object of the present invention lis to provide a novel control mechanism of the above described type which is of relatively simple and rugged construction and can be economically manufactured.

Other objects of the present invention will become apparent in the following description and the accompanying drawings, wherein:

Fig. l is a diagrammatic view illustrating a control mechanism embodying the principles of this invention;

Fig. 2 is a vertical cross-sectional view taken along line 2 2 in Fig. 3 and shows a portion of the control mechanism embodying this invention;

Fig. 3 is a horizontal cross-sectional View taken along line 3 3 in Fig. 2;

Fig. 4 is a vertical cross-sectional view taken along line 4-4 in Fig. 5 and shows a modified form of the present invention;

Fig. 5 is a horizontal cross-sectional view taken along line 5-5 in Fig. 4;

Fig. 6 is a fragmentary view similar to Fig. 5 and illustrates the operation of the novel mechanism;

Fig. 7 is a cross-sectional view similar to Fig. 2 but showing a modied form of the invention; and

Figs. 8, 9, l0 and ll are diagrammatic views illustrating the operation of the mechanism of Fig. 7 with Fig. l1 showing a further slight modification.

Refem'ng now more specifically to the drawings wherein like parts are designated by the same numerals throughout the various gures, a control mechanism 10 is illustrated in Fig. l and is connected for operating a valve 12. While for the purpose of illustrating the present invention, the control apparatus is shown and will be described for operating a valve, it is understood that the control mechanism may be applied to various uses which will readily suggest themselves.

In accordance with the present invention, the control mechanism -10 includes a novel gearing unit 14 for initially applying a relatively great torque to the valve stem 16 and then increasing the rate of operation of the valve stem. The gearing unit 14 includes a housing 18 having a power input shaft 20 journaled in Va bearing 22 on one side thereof and an output shaft 24 journaled in a bearing 26 at the opposite side thereof. It is understood that `the output shaft 24 may rbe connected directly to the valve stem or may be connected to any other Idevice to be operated. A large gear 2.8 is fixed on the input shaft 20 and may be formed integral therewith in the lmanner illustrated. A stub shaft 3i) is eccentrically located on the gear 28 and may either be formed integral with the gear or as a separate part. A cluster gear cornprising a relatively large gear portion 32 and a relatively small gear portion 34 is rotatably mounted on the lower end of the stub shaft 30. The larger gear portion 32 is disposed for meshing engagement with a gear 36 fixed to the housing 18 and the smaller gear portion 34 is disposed for meshing engagement with a gear 38 fixed to or integral with the output shaft 24. With this structure, it would seem that upon rotation of the input shaft and large gear 28, the cluster gear is carried around and driven by the iixed gear 36 so that the cluster gear portion 34 drives the output shaft. However, as shown best in Fig. 3, the teeth on the output gear 38 are interrupted as at 40 so that after a predetermined 'interval the cluster gear disengages from the output gear. In order to drive the output gear upon disengagement of the cluster gear therefrom, a lug I42 depends from the input ygear 28 and a similar lug 44 projects upwardly from the output gear 3S and these lugs are adapted to engage each other to provide a driving connection between the gears 28 and 38. Various means may be provided for driving the input gear 28 and in accordance with one form of the present invention, the gear 28 may be operated from a remote position through a flexible drive cable 46. This cable may be of any conventional construction having teeth 48, which teeth may be provided, -for example, by helically wrapping a wire around the cable. The drive cable 46 is preferably guided within the tube 50 and is 'conducted within the housing 1S through a suitable connection 52. As shown best in Fig. 3, the cable passes around the periphery of gear 28 and may exit from the housing 1S into another guide tube 54 connected to the housing by fitting 56. Suitable means 58 is provided for actuating the drive cable at a point remotely located with respect to the valve or other devices. Such means may include a housing '60 for guiding the cable and a gear 62 operable by handle 64 for actuating the cable. As will be understod, flexible cables of this type may be longitudinally actuated or they may be rotated and it is contemplated by this invention that the actuating means 58 may be of any suitable form to operate the cable in any desired manner.

With the gearing in the position shown in Figs. 2 and 3, the valve is closed and in order to open the valve, the cable 46 is actuated to rotate the input gear 28 in a counterclockwise direction as viewed in Fig. 3. Upon such counterclockwise rotation, it is seen that the lug 42 moves away from the lug 44 and that the gear 34 moves into meshing engagement with the teeth of the gear 38.

3 Upon further counterclockwise rotation, the output gear 38 is driven at a relatively slow speed and with a relatively great force by gear 34 until such time as the gear 34 substantially completely circles the gear 38, whereupon these gears will disengage from each other and the lug 42 will again engage the lug 44 to provide a direct relatively high speed drive between the input gear and the output gear. Upon reverse rotation of the gearing, it is seen that the lug 32 again moves away from the lug 44 and that the gear 34 again meshes with the gear 38 for a predetermined interval. Thus, by this structure, means has been provided whereby the output shaft may be initially driven in either direction at a relatively slow speed and a relatively great force, and after the passage of a predetermined interval, the output shaft automatically is driven at a relatively high speed.

In Figs. 4 through 6, there is illustrated a slightly modilied embodiment of the present invention which includes a gearing unit 66 that may be substituted for the above described gearing unit 14. The unit 66 includes a housing 68 with an output shaft 70 journaled in bearings 72 and 74 located at opposite sides of the housing. A ring gear 76 is secured within the housing by means of a plurality of screws 78 and a plurality of planetary gears 80 are disposed for meshing engagement with the ring gear. Each of the planetary gears 80 is rotatably mounted on a stub shaft 82 secured to a planetary gear arm 84, which planetary gear arm is fixed to the output shaft 70 by means of a pin 86 or in any other suitable manner. A sun gear 88 is rotatably mounted on the shaft 70 and is also disposed for meshing engagement with the planetary gears. This sun gear may be provided with a hub 90 which is surrounded by a bearing member 92 and a power input gear 94 is journaled on the bearing 92. The power input gear carries a pin 96 which extends upwardly through an elongated slot 98 in a lever 100. The lever 100 is rotatably mounted about the shaft 70 and carries a pawl 102 adapted to engage a ratchet wheel 104 rotatably mounted on the output shaft. In order to operate the pawl for engagement with the ratchet wheel, a leaf spring 106 connects the pawl and the pin 96. The pawl 102 is mounted on the lever 100 by means of a pin 108 and this pin extends upwardly above the lever as at 110 for driving engagement with an arm 112 fixed to the output shaft 70 in any suitable manner such as by pin 114.

The gearing unit 66 may be operated in substantially the same manner as the above described gearing unit 14 and thus the tiexible drive cable 46 is directed into a housing 68 through a fitting 116 for operative engagement with the power output gear 94, and the cable leaves the housing through a fitting 118. The output shaft 70 may be connected in any suitable manner with a valve stern or any other device to be operated and to illustrate the operation in the gearing unit 66, it is assumed that the valve is closed when the elements of the gearing unit are disposed as shown in Figs. 4 and 5. In order to open the valve, the flexible cable 46 is actuated to drive the input 94 and the pin 96 carried thereby in a counterclockwise direction as viewed in Fig. 5. As the pin passes to the end of the slot 98 in the lever 100, the pawl is tripped into engagement with the ratchet wheel so that upon further movement of the gear 94 and the pin 96, the arm 100, the pin 108, the pawl 102 and the ratchet wheel 104 are also driven in a counterclockwise direction. The ratchet wheel is provided with a hub 120 having one or more teeth 122 fitting into complementary recesses 124 in the sun gear hub to provide a driving connection between the ratchet wheel and the sun gear. Thus, as the ratchet wheel is driven in the manner just described, the sun gear is also driven in a counterclockwise direction and the sun gear drives the planetary gears, which in turn drive the output shaft 70. By referring particularly to Fig. 5, it is seen that upon the initial counterclockwise movement of the gearing, ,the upper extension 110 of the pin 108 moves away from the arm 112 so that for a predetermined interval, the only driven connection between the input gear 94 and the output shaft is through the ratchet wheel, the sun gear and the planetary gear. However, since the ratchet wheel and the arm rotate faster than the output shaft, the extension of the pin will overtake, after a predetermined interval, the arm 112 fixed on the output shaft as shown in Fig. 6. After the pin extension 110 engages the arm 112, as shown in Fig. 6, further counterclockwise rotation of the gearing causes the pin 110 to drive the arm 112 so that the output shaft is driven at an increased speed. As the speed of the output shaft is increased, the ratchet wheel is driven through the planetary gearing at an even higher speed so that the ratchet wheel overrides the pawl 102. Upon reverse rotation of the gearing to close the valve or the like, it is obvious that the pawl will be actuated to drive the ratchet wheel in a clockwise direction for a predetermined interval until the pin extension 110 advances so as to engage the arm 112 in the manner shown in Fig. 5, whereupon the pin will be effective to drive the arm in the clockwise direction.

In the gearing units described above, the maximum amount of travel or angular movement of the input shaft With the unit in low gear is approximately equal to 1 revolution plus reduction ratio minus the small angular movement loss due to the overlapping of the stops. The maximum angular movement of the output shaft with the gearing unit in low gear is approximately equal to the maximum angular movement of the input shaft multiplied by reduction ratio For example, if the reduction ratio is 10:1 then the angular movement of the output shaft is approximately .ll revolution less the loss due to the overlapping of the stops. Thus it is seen that while the input shafts of the embodments described above are rotated about one revolution the output shaft will be driven in low gear a relatively small distance depending on the particular reduction ratio of the gearing unit.

In some instances it may be desirable to increase the angular .movement of the input and output shafts while the gearing unit is in low gear without decreasing the reduction ratio of the gears. This may be accomplished by the embodiment illustrated in Figs. 7-11. In this embodiment a gearing unit is shown, which gearing unit 1s substantially identical to the gearing unit 14 described above except that the stops 42 and 44 have been eliminated and replaced `by a Geneva motion device. Thus the gearlng unit 130 includes a housing 132 and input shaft 134 having a large drive wheel 136 xed thereon and an actuator member 138 for operating the drive wheel. An eccentric pin 140 extends from the drive wheel 136 and rotatably carries a cluster gear having a large gear portion 142 and a smaller gear portion 144. The gear 142 meshes with a sun gear 146 fixed on the housing and the gear 144 meshes with a sun gear 148 fixed on a rotatable output shaft 150.

As set forth in the preceding paragraph the gearing unit 130 is provided with a Geneva motion device whereby the input shaft may be rotated two or more revolutions while the -unit is in low gear to increase the angular movement which the output shaft may be driven in low gear. This Geneva motion device includes a disc 152 fixed on the output shaft and having a single tooth 154. A cooperating disc 156 is freely rotatably mounted on the eccentric pin 140. The disc 156 is provided with one or more slots 158 adapted to mesh with the tooth 154 and a stop portion 160 adapted to engage the tooth and prevent ,fu-Tim?? Ilative rotation between the discs 152 and 156.

The Geneva motion device allows the input shaft to be rotated approximately one revolution plus one revolution for each slot 158 in the disc 156. Thus in the modiiication shown in Figs. 8, 9, and wherein the disc 156 is provided with five slots 158 the input shaft may be rotated approximately six revolutions while in low gear. The manner in which a Geneva motion device functions is well known and need not be described. However, in Figs. 8 and 10 the positions of the discs 152 and 156 are respectively illustrated at the commencement and completion of the valve opening cycle of the gearing unit and the discs are illustrated at some mid point of this cycle in Fig. 9.

Fig. 11 illustrates a modiiication of the Geneva motion device wherein the disc 156:1 is provided with a single slot 158a. With this modification the input shaft may be rorated approximately two revolutions while in low gear.

While the gearing unit of Fig. 7 which incorporates a Geneva motion device is similar to the gearing unit of Figs. 2 and 3 it is obvious that the Geneva motion device can be applied to a gearing unit of the type shown in Figs. 4 through 6 as well as to other forms of gearing units which may suggest themselves.

From the above description, it is seen that the present invention has provided a novel and relatively simple control mechanism whereby a device such as a valve may be initially operated with a relatively great force and at a relatively low speed for a predetermined interval whereupon the mechanism is automatically operable to increase the rate at which the device is operated. Furthermore, it is seen that the present invention has provided a novel control mechanism whereby a device to be operated may be actuated from a remote location.

While the preferred embodiments of the present invention have been shown and described herein, it is obvious that many structural details may be changed without departing from the spirit and scope of the appended claims. For example, it is obvious that the input gears of the novel gearing units may be driven by various means such as torsion cables or shafts, belts, gears or other well-known devices. Furthermore, it is obvious that the mechanical advantages of the novel gearing units may be changed by altering the arrangement of the gearing in ways which are readily apparent.

The invention is claimed as follows:

1. A drive mechanism comprising a power input member, a power output member, primary drive means positively driven by said input member and providing a relatively high mechanical advantage for positively driving the output member during an initial predetermined amount of movement in one direction, said primary drive means including a planetary gear system comprising first and second planet gears movable in unison and respectively paired with and engaging a first sun gear permanently iiXed to said power output member and a second permanently fixed non-rotatable sun gear, and secondary drive means positively driven by said input member and automatically operable after said predetermined amount of movement has been accomplished for positively driving said output member in said direction with reduced mechanical advantage, one gear of one of said pairs of gears having an interruption in teeth thereof located for rendering said primary drive means ineffective to drive said power output member upon operation of said secondary drive means.

2. A drive mechanism, as defined in claim 1, wherein said secondary drive means provides a direct driving connection between said power input member and said power output member.

3. A drive mechanism, as defined in claim 1, wherein said secondary drive means includes Geneva motion means connected operably with said power input member and said power output member and automatically operable after said input member has been rotated a plurality of revolutions for driving said output member in said one direction.

4. A drive mechanism as set forth in claim 1 and further including remotely disposed actuating means and a iiexible drive member connecting said actuating means and said power input member.

5. A drive mechanism as set forth in claim 4 wherein the drive member comprises a gear and the exible member is provided with projections meshing with the teeth of said gear.

References Cited in the file of this patent UNITED STATES PATENTS 149,211 Foot et al. Mar. 31, 1874 1,379,349 Leonard May 24, 1921 2,305,489 Payne Dec. 15, 1942 2,443,064 Bliss June 8, 1948 2,662,422 McGowan Mar. 24, 1952 2,757,547 Julin Aug. 7, 1956 FOREIGN PATENTS 45,565 Sweden June 5, 1918 615,612 France Ian. 12, 1927 

